• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    Maximum angular displacement between the rotatable valve elements of a steering control valve is governed solely by the circular pitch of the piston gear associated with the metering gear pump in a hydrostatic fluid power steering system. A pair of fluid collecting manifolds in the control valve respectively communicate with the expanding and contracting pockets in the gear pump to form part of the flow paths between the gear pump and the fluid power steering motor.
    公开号:SU1019998A3
    申请号:SU802885251
    申请日:1980-02-11
    公开日:1983-05-23
    发明作者:Либерт Карл-Хайнц；Тишер Вернер
    申请人:Цанрадфабрик Фридрихсхафен,Аг (Фирма)；
    IPC主号:
    专利说明:

    the collector channel is made on the outer side of the inner spool element in the form of a ring sleeve, the holes of the second row of the pope. The belts are connected to one of the two annular grooves, and the control channels of the internal rotatable spool element are formed by two rows of longitudinal grooves located on the outer side of the internal spool element, each row of which is connected to one of the aforementioned annular grooves.
    The invention relates to hydrostatic steering for vehicles and can be used in vehicles with controlled rear wheels. Hydrostatic steering of a vehicle is known, containing dosirukiye hand pump rotor-piston type with rotary-piston piston, distributor with hole for supplying the working bone, consisting of a body and two installed concentrically and with: the possibility of rotation of the outer and inner spool elements relative to each other One of which is installed in a housing connected to the metering pump and rigidly connected to a rotary piston to provide the working fluid through control channels made in the spool elements and the housing to the expanding pump sections of the metering hand pump And drain the working fluid from the converging pump sections of the said pump to the control hydraulic cylinder, and the other spool element is rigidly connected to the drive shaft, and the control channels made in the housing and leading to the depressions the stator teeth are extended to; the corresponding surface of the outer spool element with the formation of the first row of holes, and a second row of holes on the outer spool element, circulating with the first row of holes, distribution joint, the total number of holes being doubled the number of teeth of the rotary piston C1 p The disadvantage of the known steering is the impossibility of its use on any means of transport due to the occurrence of self-oscillations. The aim of the invention is an increase in the degree of unification of the steering. This goal is achieved by the fact that in the device on the inner spool element there are two collector channels, at least one of which is made in the form of an annular groove located on its outer side, the holes of the second row are alternately connected to one of two collector channels, connected to the control channels of the spool elements, the latter being formed by a reversing steering device. In addition, each second hole of the second row is made open in the face space formed by the rotating golden-metal elements and the body, which together with the internal spool element forms another collector channel, the control channels of the internal slide element being formed by longitudinal grooves. connected to an upstream / 1-groove groove and to control channels of the inner spool element. The second collector channel is made on the outer side of the inner spool element in the form of an annular groove, the holes of the second row are alternately connected to one of the two annular grooves, and the control channels of the inner rotary spool element are formed by two rows of longitudinal and anoints located on the outer side an inner spool element, each row of which is connected to one of the said annular grooves. Fig. 1 shows a hydrostatic steering, general view in Fig. 2, section A-A in Fig. 1; FIG. 3 is a section BB in FIG. one; in Fig., k is a scan of the inner and outer rotating elements (the inner element is shown by a dotted line); Fig. 5 is a scanning of the internal rotating member; in fig. 6 and 7 are the relative positions of the rotating spool elements when turning. The steering contains a dosing hand pump, distribute 2 with rotating spool, Dosing hand pump 1 of rotary piston type has a stator 3 with seven teeth k, and also a rotary piston 5 with six teeth 6, Between the teeth there are isolated from the other pump sections 7 ,. of which, with rotation, in each case about half expands, the remainder narrows. The metering hand pump 1 is fastened to the casing 9 of the distributor 2 with the rotating spool using threaded bolts 8. From the cavities 10 between the stator teeth 3, seven housing channels 11, $ that surround seven threaded fingers 8 lead to the first crown of the seven control channels 12, which open against the central opening 13 of the housing 9 in this central hole with a small gap with the possibility of free installation of an externally rotating spool element 1A in the central hole of this rotating spool element with a small clearance, the internal rotating spool element 15 is installed. growing relative to each other against the action of the centering spring 1b. The inner rotating spool element is integral with the drive 17, which is rigidly connected to the steering shaft. The external rotating spool element is connected to the rotor piston rigidly with respect to rotation, but movably in the radial direction. A free face space 19 is located to the left of both rotating golden elements, which is connected to the internal space 20 of the internal rotating rotary element. Both together form a collector channel 21. In the outer rotating spool element 1k there are six evenly distributed through control holes 22, which cooperate with the control holes 12 in the housing to connect both groups of pump sections. The outer rotary valve also has six, installed in each case in the center between the control holes 22, and the control holes 23 in the form of longitudinal grooves. The control apertures 22 and 23 form together a second crown and interact with the control apertures 12 of the first crown. The control holes 23 open against the face space 19 and are thus communicated with the collector channel 21. The inner spool element 15 has an annular groove 2. which communicates with the control holes 22 of the external rotary slide element. This annular groove forms the second collector channel. Due to this construction, in each case one of the groups of pump sections (for example, expanding) is in communication with one of the collector channels 21, which includes the inner space 20, and another with the other collector channel, namely the annular groove 2. In the housing for supplying the working fluid from the high-pressure pipeline 25, annular grooves 26 and 27 are provided, which are connected to both working chambers of the control hydraulic cylinder 28. The inner rotating spool member 1 (Fig. 5) has four outer longitudinal grooves 29, which are evenly distributed around the perimeter and communicated with the annular groove 2. There are through holes 30 in the center between the longitudinal grooves 29. Through holes are called radially passes through the rotating spool element, i.e. they lead from its outer to its inner wall, and the grooves lead to channels that are provided only on the outer side of the rotating spool element, but do not extend to its inner wall. The inner rotating spool element has longitudinal grooves 31, which are mounted on one straight line coaxially with through holes 50, and through open holes 32, which are mounted on one straight line coaxially with longitudinal grooves 29. External rotating spool element (Fig. 4 ) has control holes 23 in the form of longitudinal grooves that open to the end space. In the outer rotating spool element, with several axial spacings, the rims are fitted with apertures 33 and 3, which are connected by means of body annular grooves 35 or 36 to the high-pressure pipeline 25, the distal holes 37 and 38 are offset along the perimeter relative to each other and through the case annular grooves 2b and 27 are connected to both working chambers of the control hydraulic cylinder 28, and finally through holes 39 in the form of elongated decoctions passing along the perimeter, which COROLLARY housing annular groove 40 communicated with the return line k, longitudinal grooves C2 on the decomposition in any rotation are connected via through-holes 39 with return line tl, i.e. themselves are part of the return pipeline. In the neutral position (Fig. 4), the working fluid flows from the high pressure pipeline 25 through the through holes 3k to the longitudinal grooves K2 and through the through holes 39 to the return pipe 41. When the steering wheels turn, this neutral flow more and more intersects and finally , completely overlaps. The mutual position of the rotating spool elements when turning for the sake of simplicity is shown in both edges of them. Neutral leakage is interrupted due to the fact that the through holes 3 are located outside the longitudinal grooves 42. At the turning position shown in FIG. 6, the working fluid flows through the through holes 33 in the outer rotatable spool element. 29, from there into its annular groove 24 therefrom, through the control holes 22 in the outer rotatable spool element and part of the body channels 43 to one of the groups of pump sections. The working fluid returning from another group of pumping sections flows through the remaining housing channels 43 and the control holes 23 of the external rotating spool element to the front space 19 and the internal space 20 and from there, through the through holes 32 of the internal rotating spool element, to the right working chamber of the hydraulic cylinder 28 controls From the left working chamber, the working fluid flows to the squamous holes 37 in the outer rotating spool element and through them to the longitudinal canars 42 in the inner rotating spool element, and thereby to the return pipe. When the steered wheels are turned in the opposite direction, the position of both rotating spool elements is obtained (again in the extreme position) (Fig. 7). From the high pressure pipeline 25, the working fluid flows through the now overlapping through holes 33 and 30 to the inner space 20, through the end space and control holes 23 in the outer rotating spool element to one of the groups of pump sections. The working fluid flowing back through the through holes 22 in the outer rotatable spool element falls into and out of the annular groove 24. into the longitudinal grooves 29. Of them, it flows through the through holes 37 in the outer rotating spool element to one of the working chambers of the control hydraulic cylinder (acting opposite to that in comparison with Fig. 6). From another working chamber, the returning fluid flows through the through-holes. 38 in the outer rotatable GOLDEN ELEVATOR to the longitudinal grooves 42 in the inner rotatable spool member, and thus in the return pipeline. This makes it possible to increase the degree of unification of the steering. J. J. t-K Qi9ai} 3 ms
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    权利要求:
    Claims (3)
    [1]
    1. HYDROSTATIC STEERING VEHICLE, comprising a rotary piston type metering manual pump with a gear rotary piston, a distributor
    With holes for supplying a working fluid, a bone, consisting of a housing and two concentric and rotatably mounted relative to each other outer and inner spool elements, one of which is installed in a housing connected to a subsidizing hand pump and rigidly connected to a rotary piston to provide a working piston fluid through control channels made in spool elements and casing to the expanding pump sections of the dosing hand pump and drainage of the working fluid from the contracting pump sec of the aforementioned pump to the control hydraulic cylinder ^ and another spool element is rigidly connected to the drive shaft, and the control channels made in the housing and leading to the hollows between the stator teeth are extended to the corresponding surface of the outer spool element with the formation of the first row of holes, and on the outer spool the element has a second row of holes, forming a distribution connection with the first row of holes, while the total number of holes is made equal to twice the number of teeth rotor about the piston, it is noteworthy that, in order to increase the degree of unification of the steering, two collector channels are made on the internal spool element, at least one of which is made in the form of an annular groove located on its outer side, holes the second row are alternately connected to one of the two collector channels connected to the control channels of the spool elements, the latter forming a reversing steering device.
    [2]
    2. The control according to claim 1, characterized in that, each second hole of the second row is made * unopened into the end space formed by the rotating spool elements and the housing, which together with the internal spool element forms another collector channel moreover, the control channels of the inner spool element are formed by longitudinal grooves connected to the said annular groove and with the control channels of the inner spool element,
    [3]
    3. Management by π. 1, it is noteworthy that the second collector channel is made on the outer side of the inner spool element in the form of an annular groove, the holes of the second row are alternately connected to one of the two annular grooves, and the control channels are internal The rotating spool element is formed by two rows of longitudinal grooves located on the outer side of the inner spool element, each row of which is connected to one of the aforementioned ring grooves.
    类似技术:
    公开号 | 公开日 | 专利标题
    US3895888A|1975-07-22|Hydrostatic control unit
    US2570411A|1951-10-09|Power transmission
    US4109679A|1978-08-29|Controller for fluid pressure operated devices
    US3561893A|1971-02-09|Hydrostatic control equipment' partic-ularly for steering systems
    US3270683A|1966-09-06|Porting arrangement for balancing valve of fluid pressure device
    US3516769A|1970-06-23|Rotary vane hydraulic motor
    US4311171A|1982-01-19|Hydrostatic steering controller with pressure dams
    SU1019998A3|1983-05-23|Hydrostatic steering system of vehicle
    SU1041044A3|1983-09-07|Hydrostatic regulator
    GB1299380A|1972-12-13|Improvements in or relating to rotary positive-displacement hydraulic pump or motor assemblies
    US6544018B2|2003-04-08|Hydraulic motor having multiple speed ratio capability
    SU1022668A3|1983-06-07|Hydraulic rotary servo drive
    US4671747A|1987-06-09|Control device for hydrostatic power assisted steering
    US4470432A|1984-09-11|Distributor for a hydraulic servo mechanism
    US3887308A|1975-06-03|Valve porting arrangement for a gerotor
    US3598509A|1971-08-10|Hydraulic device
    US5137438A|1992-08-11|Multiple speed fluid motor
    US4579040A|1986-04-01|Power steering device
    USRE31067E|1982-10-26|Hydrostatic control unit
    US3584985A|1971-06-15|Hydrostatic control equipment particularly for steering systems
    US4499922A|1985-02-19|Rotary distributor for a hydraulic servo-mechanism
    SU1090268A3|1984-04-30|Rotary hydraulic pilot directional valve
    US4184813A|1980-01-22|Fluid rotating machine with multiple displacement
    US3425448A|1969-02-04|Fluid pressure balanced valve
    US4527591A|1985-07-09|Hydraulic rotary distributor with a star-shaped rotor, more particularly for a power-assisted steering mechanism
    同族专利:
    公开号 | 公开日
    FR2449019A1|1980-09-12|
    JPS55110664A|1980-08-26|
    GB2043001B|1983-08-17|
    BR8000920A|1980-10-29|
    JPH0341385B2|1991-06-21|
    DE2906183A1|1980-08-21|
    FR2449019B1|1985-02-22|
    DE2906183C2|1986-09-18|
    GB2043001A|1980-10-01|
    SE8001229L|1980-08-18|
    US4395877A|1983-08-02|
    DD149050A5|1981-06-24|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    US3438200A|1967-03-31|1969-04-15|Int Harvester Co|Power steering with directional admittance and poppets|
    US3587235A|1969-06-02|1971-06-28|Trw Inc|Regenerative hydrostatic steering system|
    US3819307A|1972-10-24|1974-06-25|Eaton Corp|Stability means for a controller for fluid pressure operated devices|
    DE2253575C3|1972-11-02|1975-04-24|Danfoss A/S, Nordborg |Hydraulic control devices for steering systems, in particular for vehicle steering systems|
    JPS4996220U|1972-12-07|1974-08-20|
    US4033377A|1974-09-18|1977-07-05|Eaton Corporation|Controller for fluid pressure operated devices|
    GB1524707A|1974-09-18|1978-09-13|Eaton Corp|Controller for fluid pressure operated devices|
    DE2637332C3|1976-08-19|1981-04-23|Danfoss A/S, 6430 Nordborg|Hydraulic power steering device|FR2514433B1|1981-10-09|1983-12-23|Dba|
    DD250510B5|1984-04-24|1994-03-31|Hydraulik Nord Gmbh|HYDROSTATIC STEERING DEVICE|
    DD224287A1|1984-06-13|1985-07-03|Sasnowski Hydraulik Nord|HYDROSTATIC STEERING DEVICE|
    DE3626381A1|1985-08-06|1987-02-12|White Jun Hollis Newcomb|Hydrostatic steering device|
    US5080135A|1990-10-24|1992-01-14|Eaton Corporation|Large deflection angle rotary modulation steering valve|
    DE102020106438A1|2020-03-10|2021-09-16|Danfoss Power Solutions Aps|Fluid control device, in particular as part of a hydraulic steering unit|
    DE102020106437A1|2020-03-10|2021-09-16|Danfoss Power Solutions Aps|Fluid control device, in particular as part of a hydraulic steering unit|
    法律状态:
    优先权:
    申请号 | 申请日 | 专利标题
    DE2906183A|DE2906183C2|1979-02-17|1979-02-17|Hydrostatic steering device for automobiles|
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